ES2705082T3 - Air conditioner - Google Patents

Abstract

An air conditioner (1) comprising: a compressor (10) for compressing a refrigerant, the compressor having a suction unit (10a) and a plurality of injection inlets (11, 12, 13); an indoor heat exchanger (40) into which the compressed refrigerant is introduced during a heating operation; an outdoor heat exchanger (20) into which the compressed refrigerant is introduced during a cooling operation; a plurality of refrigerant separation devices (50, 60, 70) through which a condensed refrigerant passes in the indoor heat exchanger or the outdoor heat exchanger; a plurality of injection flow paths (51, 61, 71) extending from the plurality of refrigerant separation devices (50, 60, 70) towards the plurality of injection inlets (11, 12, 13); and a bypass flow path (80) extending from one of the plurality of injection flow paths (51, 61, 71) towards the suction unit (10a), wherein the plurality of inlets (11, 12 injection) comprises a first injection inlet (11) and a second injection inlet (12), the plurality of refrigerant separation devices (50, 60) include a first indoor heat exchanger (50) and a second indoor exchanger (60) heat, and the plurality of injection flow paths (51, 61) includes a first injection flow path (51) and a second injection flow path (61), characterized in that: the plurality of Injection inlets (11, 12, 13) further comprises a third injection inlet (13), the plurality of refrigerant separation devices (50, 60, 70) further includes a third indoor heat exchanger (70), and the plurality of injection flow paths (51, 61, 71) further includes a third r injection flow path (61), wherein said first injection flow path (51) is connected to the first indoor heat exchanger (50) to inject into the compressor (10) a refrigerant having a first intermediate pressure; said second injection flow path (61) is connected to the second indoor heat exchanger (60) to inject into the compressor (10) a refrigerant having a second intermediate pressure; and said third injection flow path (71) is connected to the third indoor heat exchanger (70) to inject into the compressor (10) a refrigerant having a third intermediate pressure, and the second intermediate pressure is higher than the first intermediate pressure and the third intermediate pressure is higher than the second intermediate pressure.

Description

DESCRIPTION

Air conditioner

In the present document, an air conditioner is described.

Air conditioners are devices to maintain a desired air temperature in a room. For example, the air conditioner can work to cool the room, to heat the room and to adjust the humidity of the room. In particular, the air conditioner drives a refrigeration cycle in which the compression, condensation, expansion and evaporation of a refrigerant is carried out, and therefore can perform a cooling or heating operation of the room.

The air conditioner may be a separate type air conditioner in which an indoor unit and an outdoor unit are separated, or an integrated air conditioner in which the indoor unit and the outdoor unit are combined. The outdoor unit typically includes an outdoor heat exchanger that exchanges heat with the outside air, and the indoor unit typically includes an indoor heat exchanger that exchanges heat with the indoor air. The air conditioner can be operated in cooling mode or in heating mode.

When the air conditioner is operated in the cooling mode, the outdoor heat exchanger functions as a condenser and the indoor heat exchanger functions as an evaporator. On the contrary, when the air conditioner is operated in the heating mode, the outdoor heat exchanger functions as an evaporator, and the indoor heat exchanger functions as a condenser.

In general, when the temperature of the outdoor air where the air conditioner is installed is higher or lower than a set temperature, a sufficient amount of refrigerant circulation must be ensured to achieve the desired cooling and heating performance. This usually requires a large capacity compressor, which is expensive to manufacture and install.

To solve this problem, systems have been developed by which refrigerant is injected into a spiral compressor using a refrigerant injection flow path. See, for example, Korean application No. 10-1280381. For example, as described in Korean application No. 10-1280381, first and second coolant injection nozzles are formed. The mouths allow to inject refrigerant twice while the refrigeration cycle is carried out. However, when the outside air temperature is too high or too low, it is difficult to achieve the sufficient amount of refrigerant circulation to guarantee the desired cooling and heating performance using only two injections.

EP 2631 563 A1 relates to an air conditioner including a compressor, an outdoor heat exchanger, an indoor heat exchanger and an expansion device including an overcooler device for supercooling a condensed refrigerant in the exchanger of heat from outside or in the indoor heat exchanger, an injection conduit through which the refrigerant passing through the supercooler device is introduced into an incoming flow part by injection into the compressor, a bypass line extending from the injection conduit to a suction part of the compressor for bypassing the refrigerant, and an opening / closing part of the conduit disposed in at least one of the injection conduit and the bypass conduit, to selectively block a flow of the refrigerant.

EP 2631563 A1 discloses an air conditioner according to the preamble of claim 1.

To solve the aforementioned problem, an air conditioner is provided according to claim 1. Embodiments will be described in detail with reference to the following drawings, in which similar reference numerals refer to similar elements, and wherein:

Figure 1 is a system diagram illustrating a configuration of an air conditioner according to a first embodiment;

Figure 2 is a cross-sectional view illustrating a configuration of a compressor according to the first embodiment; Figure 3 is a view illustrating an arrangement of a spiral envelope and an injection inlet in a compressor according to the first embodiment;

Figure 4 is a graph illustrating the variation of performance as a function of the angle of a rotating axis of rotation while the second and third injection inlets are open simultaneously, according to the first embodiment; Figure 5 is a graph illustrating the manner in which the internal pressures of the first and second compression chambers vary according to the first embodiment, as a function of the angle of the axis of rotation;

Figure 6 is a system diagram illustrating a flow state of a refrigerant during heating operation of an air conditioner according to the first embodiment;

Figure 7 is a diagram illustrating a flow state of a refrigerant during cooling operation of an air conditioner according to the first embodiment; Y

Figure 8 is a system diagram illustrating a configuration of an air conditioner according to a second embodiment.

In the following, embodiments will be described in detail, with reference to the accompanying drawings. However, the embodiments may be executed in many different ways, and should not be construed as being limited to the embodiments set forth herein; rather, alternative embodiments that are within the scope of the claims will convey the concept entirely to those skilled in the art.

Figure 1 is a system diagram illustrating an air conditioner according to a first embodiment.

Referring to Figure 1, an air conditioner 1 according to a first embodiment drives a refrigeration cycle in which a refrigerant circulates. The air conditioner 1 can perform a cooling or heating operation according to the flow direction of the refrigerant.

The air conditioner 1 includes a compressor 10 for compressing the refrigerant, a flow path switching unit 15 for changing the flow direction of the refrigerant discharged from the compressor 10 depending on whether it is cooling operation or heating operation , an external heat exchanger 20 or an indoor heat exchanger 40 for condensing the compressed refrigerant in the compressor 10, a first expansion device 30 and a second expansion device 35, which are arranged between the heat exchanger 20 and the interior heat exchanger 40, for expanding the refrigerant, and a refrigerant pipe 90 for connecting these components and guiding a flow of refrigerant.

The air conditioner 1 further includes an outdoor fan 25 which is installed on one side of the outdoor heat exchanger 20 and blows outside air to the outdoor heat exchanger 20, and an indoor fan 45 which is installed on one side of the indoor heat exchanger 40. of heat and blows indoor air to the indoor heat exchanger 40.

When the air conditioner 1 performs cooling operation, the refrigerant is compressed in the compressor 10 and then condensed in the heat exchanger 20 through the flow path switching unit 15. The refrigerant is then expanded in the second expansion device 35 and subsequently evaporated in the indoor heat exchanger 40.

As an alternative, when the air conditioner 1 performs the heating operation, the refrigerant is compressed in the compressor 10 and then condensed in the indoor heat exchanger 40 via the flow path switching unit 15. The refrigerant is then expanded in the first expansion device 30 and subsequently evaporated in the heat exchanger 20.

Thus, during a cooling operation the outdoor heat exchanger 20 functions as a condenser and the indoor heat exchanger 40 functions as an evaporator, and during a heating operation the indoor heat exchanger 40 functions as a condenser and the outdoor exchanger 20 of heat works like an evaporator.

In the following, an example of a case in which the air conditioner 1 performs cooling operation will be described.

The compressor 10 is configured to perform a multi-stage compression. For example, the compressor 10 may include a scroll compressor for compressing the coolant by a relative phase difference between a fixed scroll and an orbiting scroll.

The air conditioner 1 includes a plurality of internal heat exchangers 50, 60 and 70 for supercooling the refrigerant that has passed through the condenser.

For example, in the case of cooling operation, the plurality of internal heat exchangers 50, 60 and 70 includes a first internal heat exchanger 50 for supercooling the refrigerant that has passed through the heat exchanger 20, a second exchanger interior 60 of heat to supercool the refrigerant that has passed through the first internal heat exchanger 50 and a third internal heat exchanger 70 to supercool the refrigerant that has passed through the second interior heat exchanger 60. The first, second and third internal heat exchangers 50, 60 and 70 may be connected in series. For their part, the first, second and third internal heat exchangers 50, 60 and 70 operate to supercool the refrigerant and, therefore, can be referred to respectively as first, second and third supercoolers 50, 60 and 70.

The air conditioner 1 includes a first injection flow path 51 through which some refrigerant from the refrigerant that has passed through the heat exchanger 20 is derived to the compressor 10 and a first expansion unit 55 of injection which is located in the first injection flow path 51 and adjusts the quantity of the derived refrigerant. The refrigerant can expand as it passes through the first injection expansion unit 55. For example, the first injection expansion unit 55 may include an electronic expansion valve (EEV).

The refrigerant derived to the first injection flow path 51 from between the refrigerant that has passed through the heat exchanger 20 is referred to as the "first diverted refrigerant", and the remaining refrigerant that is not the diverted refrigerant is referred to as "refrigerant". principal". In the first heat exchanger 50 heat exchange takes place between the main refrigerant and the first diverted refrigerant.

Since the first diverted refrigerant is converted to low temperature and low pressure refrigerant when it passes through the first injection expansion unit 55, the first diverted refrigerant absorbs heat while exchanging heat with the main refrigerant and the main refrigerant transmits heat to the main refrigerant. deviated first refrigerant. Therefore, the main refrigerant may be overcooled. In addition, the first diverted refrigerant passing through the first heat exchanger 50 can be injected into the compressor 10 through the first injection flow path 51.

The compressor 10 includes a first injection inlet 11 connected to the first injection flow path 51. The first injection inlet 11 is located in a first position of the compressor 10.

The air conditioner 1 includes a second injection flow path 61 through which some refrigerant is diverted between the main refrigerant which has passed through the first heat exchanger 50, and a second injection expansion unit 65. which is located in the second injection flow path 61 and adjusts the amount of the derived refrigerant. The refrigerant can expand as it passes through the second injection expansion unit 65. For example, the second injection expansion unit 65 may include an EEV.

The refrigerant derived to the second injection flow path 61 is referred to as the "second diverted refrigerant". Heat exchange between the main refrigerant and the second diverted refrigerant takes place in the second internal heat exchanger 60.

Since the second diverted refrigerant is converted to low temperature and low pressure refrigerant when it passes through the second injection expansion unit 65, the second diverted refrigerant absorbs heat while exchanging heat with the main refrigerant and the main refrigerant transmits heat to the main refrigerant. second diverted refrigerant. Therefore, the main refrigerant may be overcooled. In addition, the second diverted refrigerant passing through the second ^{internal heat exchanger 60 can be injected into the compressor 10 through the second injection flow path} 61 ^. The compressor 10 includes a second injection inlet 12 connected to the second injection flow path 61. The second injection inlet 12 is located in a second position of the compressor 10. That is to say, the first injection inlet 11 and the second injection inlet 12 are connected to different positions of the compressor 10.

The air conditioner 1 includes a third injection flow path 71 through which some refrigerant is diverted between the main refrigerant that has passed through the second interior heat exchanger 60, and a third injection expansion unit 75. which is located on the third injection flow path 71 and adjusts the amount of the derived refrigerant. The refrigerant can expand while passing through the third injection expansion unit 75. For example, the third injection expansion unit 75 may include an EEV.

The refrigerant derived to the third injection flow path 71 is referred to as the "third diverted refrigerant". Heat exchange between the main refrigerant and the third diverted refrigerant takes place in the third indoor heat exchanger 70. Since the third diverted refrigerant is converted to low temperature and low pressure refrigerant when it passes through the third injection expansion unit 75, the third diverted refrigerant absorbs heat while exchanging heat with the main refrigerant and the main refrigerant transmits heat to the main coolant. diverted third refrigerant. Therefore, the main refrigerant may be overcooled.

During heating operation, the third diverted refrigerant passing through the third indoor heat exchanger 70 can be injected to the compressor 10 through the third injection flow path 71.

The compressor 10 includes a third injection inlet 13 connected to the third injection flow path 71. The third injection inlet 13 is located in a third position of the compressor 10. That is to say, the third injection inlet 13 is located in a position different from the first and second injection inlets 11 and 12.

An injection valve 78 may be installed in the third injection flow path 71, for selectively injecting the refrigerant through the third injection flow path 71. The injection valve 78 may be disposed between a branch unit 73 and the third injection inlet 13. For example, injection valve 78 may include an EEV.

During cooling operation, when the injection valve 78 is closed, the refrigerant flowing to the third injection inlet 13 may be limited and may flow to a bypass flow path 80. On the other hand, during heating operation, when the injection valve 78 is open the coolant can be injected into the third injection inlet 13. In this case, the refrigerant can be decompressed while passing through the injection valve 78.

The third injection flow path 71 is connected to the bypass flow path 80 in which the refrigerant that is introduced into the third injection flow path 71 circuits the aspiration unit 10a of the compressor 10. In particular, the unit 73 The branch path is located at a point of the third injection flow path 71, and the bypass flow path 80 extends from the branch unit 73 to the suction unit 10a of the compressor 10. The bypass flow path 80 includes a combination unit 83 connected to the suction unit 10a of the compressor 10.

A bypass valve 85 is installed in the bypass flow path 80 to selectively open and close the bypass flow path 80. The bypass valve 85 is disposed between the branch unit 73 and the suction unit 10a of the compressor 10.

Depending on the state of opening and closing of the injection valve 78 or of the bypass valve 85, the refrigerant which is introduced into the third injection flow path 71 can be injected to the compressor 10 in the third injection inlet 13 through of the injection valve 78, and sucked into the compressor 10 in the suction unit 10a through the bypass valve 85.

On the other hand, the main refrigerant that passes through the third interior heat exchanger 70 can expand while passing through the second expansion device 35, and then can flow to the indoor heat exchanger 40. In addition, the refrigerant evaporated in the indoor heat exchanger 40 can be sucked into the suction unit 10a of the compressor 10 through a flow switching unit 15. The described flow direction of the refrigerant in the foregoing has been defined based on the cooling operation, and works in reverse in the heating operation.

Figure 2 is a cross-sectional view illustrating a configuration of a compressor according to a first embodiment and Figure 3 is a view illustrating an arrangement of a spiral envelope and an injection inlet in a compressor according to a first embodiment.

Referring to Figure 2, a scroll compressor 10 includes a housing 110, a discharge cover 112 that closes an upper side of the housing, and a base cover 116 that is located on a lower side of the housing 110 and stores oil. A suction unit 10a is coupled to the discharge cap 112. The suction unit 10a extends downwards passing through the discharge cover 112, and is connected to a fixed spiral 120.

The scroll compressor 10 includes a motor 160 that is included in the housing 110 and generates a rotational force, a rotating shaft 150 that rotates and simultaneously passes through the center of a motor 160, a main frame 140 that supports a upper part of rotation shaft 150, and a compression unit which is located on an upper side of main frame 140 and compresses a refrigerant.

The motor 160 includes a stator 161 coupled to an inner circumferential surface of the housing 110, and a rotor 162 that rotates within the stator 161. The rotation shaft 150 is disposed so as to pass through a central portion of the rotor 162. In the central part of the rotation shaft 150, an oil supply flow path 157 is made so that it is eccentric with respect to either side, and thus the oil entering the oil supply flow path 157 is elevated by the centrifugal force generated by the rotation of the rotation axis 150.

An oil supply unit 155 is coupled to a lower side of the rotation shaft 150 and moves the oil stored in the cap 116 of the base to the oil supply flow path 157, while rotating in a manner integral with the shaft 150. of rotation.

The compression unit includes the fixed scroll 120 which is installed on an upper surface of the main frame 140 and is connected to the suction unit 10a, an orbiting scroll 130 meshed with the fixed scroll 120 to form a compression chamber and be supported by pivotally on the upper surface of the main frame 140, and an Oldham ring 131 which is installed between the orbiting scroll 130 and the main frame 140, and performs an orbiting movement around the orbiting scroll 130 while preventing rotation of the orbiting spiral 130. The orbiting scroll 130 is coupled to the rotation shaft 150 to receive a rotational force from the rotation axis 150.

The fixed scroll 120 and the orbiting scroll 130 are arranged so that they have a phase difference of 180 degrees to each other. In the fixed scroll 120 there is located a fixed spiral envelope 123 having a spiral shape, and in the orbiting scroll 130 an orbiting spiral envelope 132 having a spiral shape is located. For convenience, the fixed spiral 120 is referred to as the "first spiral" and the orbiting spiral 130 is referred to as the "second spiral". In addition, the envelope 123 of the fixed scroll is referred to as the "first envelope" and the envelope 132 of the orbiting scroll is referred to as the "second envelope".

The compression chamber can be formed plurally by the engagement of the envelope 123 of the fixed scroll and the envelope 132 of the orbiting scroll. The refrigerant which is introduced into the plurality of compression chambers 181 and 183 by the orbiting movement of the orbiting scroll 130 may be compressed at high pressure. In addition, a discharge orifice 121 in which the high pressure compressed refrigerant and the oil fluid are discharged is practiced near a central part of an upper part of the fixed scroll 120.

In particular, in the plurality of compression chambers 181 and 183, their volume is reduced by the orbiting movement of the orbiting scroll 130, while moving centrally from the outside of the fixed scroll 120 towards the discharge orifice 121, and the refrigerant is compressed in the reduced volume and then discharged to the outside of the fixed scroll 120 through the discharge orifice 121.

The fluid discharged through the discharge orifice 121 enters the interior of the housing 110 and is then discharged through the discharge line 114. The discharge pipe 114 may be connected to one side of the housing 110.

On the other hand, a first injection inlet 11, a second injection inlet 12 and a third injection inlet 13 are connected to the compressor 10. The first to third injection inlets 11, 12 and 13 may be spaced from each other and each of them may be connected to the discharge cover 112.

In particular, on a side surface of the discharge lid 112 the first injection inlet 11 passes through the discharge lid 112 to be inserted into the fixed spiral 120. On another side surface of the discharge lid 112, the second inlet 12 of injection passes through the discharge cover 112 to insert in the fixed spiral 120. In addition, in another side surface more of the discharge cover 112, the third injection inlet 13 passes through the discharge cover 112 for inserted in the fixed spiral 120.

The first to third injection inlets 11, 12 and 13 can be arranged being spaced apart from each other by an established angle based on the compression direction of the coolant or in the direction opposite to the compression direction.

In the fixed scroll 120 a plurality of injection ports 11a, 12a and 13a are injected to inject the coolant into a plurality of compression chambers.

The plurality of injection orifices 11a, 12a and 13a includes a first injection orifice 11a connected to the first injection inlet 11, a second injection orifice 12a connected to the second injection inlet 12 and a third injection orifice 13a connected to the injection inlet 11a. the third injection inlet 13. For example, the first injection inlet 11, the second injection inlet 12 and the third injection inlet 13 can be inserted into the injection ports 11a, 12a and 13a, respectively. While the orbiting scroll 130 rotates, the envelope 132 of the orbiting scroll selectively opens and closes the first injection orifice 11a, the second injection orifice 12a or the third injection orifice 13a.

In particular, when the envelope 132 of the orbiting scroll is located in the first position or the rotation axis 150 is at a first angle, the refrigerant sucked through the suction unit 10a enters an open space formed by the envelope 123 of the fixed scroll and the envelope 132 of the orbiting scroll.

Furthermore, when the orbiting scroll 130 performs its orbiting motion continuously, the open space is occluded by the envelope 132 of the orbiting scroll to complete a suction chamber. In this case, the suction chamber is understood as a storage space in a state in which the suction of the refrigerant is completed, and when the orbit of the orbiting coil 132 realizes its orbiting movement, the suction chamber is transformed into a chamber Of compression.

When the orbiting scroll 130 performs its orbiting motion continuously, the aspiration chamber can be compressed as it moves from the outer region of the fixed scroll 120 to the internal region thereof. In this case, the compression chamber can move in a counterclockwise direction.

The compression chamber moves towards the discharge orifice 121, and the refrigerant is discharged through the discharge orifice 121 when the compression chamber reaches the discharge orifice 121. In this way, the orbiting movement of the orbiting scroll 130 repeatedly causes the formation of the compression chamber and the compression of the refrigerant.

In the compression of the refrigerant, on the other hand, the refrigerant of the first to third paths, 51, 61 and 71, of flow injection is selectively injected into the plurality of compression chambers through the first injection inlet 11, the second injection inlet 12 or third injection inlet 13.

In the orbiting movement of the orbiting scroll 130, the envelope 132 of the orbiting scroll moves to selectively open or close the first injection orifice 11a, the second injection orifice 12a or the third injection orifice 13a. In a state in which the compression chamber moves towards one side of the first injection orifice 11a, the second injection orifice 12a or the third injection orifice 13a, when the first injection orifice 11a is opened, the second orifice 12a of injection or the third injection hole 13a, the coolant can be injected into the corresponding compression chamber. For example, the refrigerant injected through the first injection inlet 11 may be configured to have a first intermediate pressure, and may be injected into the compression chamber before the refrigerant is compressed to a greater degree in the compression chamber. . For its part, the refrigerant injected through the second injection inlet 12 can be configured to have a second intermediate pressure (greater than the first intermediate pressure), and can be injected into the compression chamber in a state in which the Coolant is compressed relatively to a greater degree in the compression chamber.

In addition, the refrigerant injected through the third injection inlet 13 may be configured to have a third intermediate pressure (greater than the second intermediate pressure), and may be injected into the compression chamber in which the refrigerant is compressed in a greater degree when compared to the compression chamber in which the refrigerant is injected through the first and second injection inlets 11 and 12.

Therefore, the first injection hole 11a is made in a position relatively far from the discharge orifice 121 in a radial direction. For its part, the second injection orifice 12a can be made in a position closer to the discharge orifice 121, in a radial direction, that the first injection orifice 11a and the third injection orifice 13a can be formed in a closer position with respect to the discharge orifice 121, in a radial direction, than the second injection orifice 12a.

Depending on the positions of the first, second and third inlets 11, 12 and 13 of injection, that is, the positions of the first, second and third holes, 11a, 12a and 13a, of injection, change the degrees of opening of the first, second and third holes, 11a, 12a and 13a, of injection when the refrigerant is injected into the compression chamber.

For example, the position of the compression chamber changes continuously as a function of the orbiting movement of the envelope 132 of the orbiting scroll, and the first, second and third holes, 11a, 12a and 13a, of injection may be in a fully closed state , in an open state of about 50% or in a fully open state, depending on the positions in which the first, second and third holes, 11a, 12a and 13a, of injection are made, based on a predetermined position of the chamber Of compression.

On the other hand, the positions of the first, second and third injection entries 11, 12 and 13 can be understood as the concept of whether the injection entry can be open when the orbiting scroll 130 rotates to a certain degree based on the time point in which the suction of the refrigerant has been completed through the refrigerant suction unit 10a. In this case, the degree to which the orbiting scroll 130 rotates may correspond to the degree to which the rotation axis 150 rotates.

In other words, the embodiment of the present description specifies the positions of the first, second and third injection inlets 11, 12 and 13 or the positions of the first, second and third holes, 11a, 12a and 13a, of injection with respect to whether the injection is effected or not through the first injection inlet 11, the second injection inlet 12 or the third injection inlet 13 when the refrigerant is compressed to a certain degree, based on the time point at which it is sucked the refrigerant through the refrigerant suction unit 10a.

Referring to Figure 3, a plurality of compression chambers are formed by the engagement of the orbiting scroll 130 and the fixed scroll 120 according to the embodiment of the present disclosure. Furthermore, the volumes of the plurality of compression chambers are reduced because of the orbiting movement of the orbiting scroll 130 while moving from the outer part of the fixed scroll 120 toward the center.

For example, the plurality of compression chambers includes a first compression chamber 181 and a second compression chamber 183. Depending on the orbiting movement of the envelope 132 of the orbiting scroll, the first compression chamber 181 and the second compression chamber 183 rotate counterclockwise, with a phase difference of approximately 180 °. It results in the refrigerant in the second compression chamber 183 having a higher pressure than the refrigerant in the first compression chamber 181.

Also, while the first and second compression chambers 181 and 183 rotate, when the envelope 132 of the orbiting scroll opens the first injection orifice 11a, the second injection orifice 12a or the third injection orifice 13a, the coolant can be injected in the first compression chamber 181 or in the second compression chamber 183.

In particular, while the first compression chamber 181 rotates counterclockwise, when the first compression chamber 181 is located on one side of the first injection inlet 11 and the first injection orifice 11a is opened, the refrigerant in the first compression chamber 181 through the first injection hole 11a.

In this case, the opening and closing of the first injection orifice 11a refers to a gradual opening and closing of the first injection orifice 11a as a function of the orbiting movement of the envelope 132 of the orbiting scroll, rather than an idea of everything or nothing. After the coolant is injected into the first compression chamber 181, compression continues as the first compression chamber 181 moves counterclockwise.

On the other hand, while the second compression chamber 183 rotates counterclockwise, when the second compression chamber 183 is located on one side of the second injection inlet 12 and the second injection orifice 12a is opened, the refrigerant can be injected. in the second compression chamber 183 through the second injection orifice 12a.

Similarly, the opening and closing of the second injection orifice 12a refers to a gradual opening and closing of the second injection orifice 12a as a function of the orbiting movement of the envelope 132 of the orbiting scroll, rather than an all-or-nothing idea. Once the refrigerant is injected into the second compression chamber 183, compression continues while the second compression chamber 183 moves counterclockwise.

While the second compression chamber 183 rotates counterclockwise, when the second compression chamber 183 is placed in the third injection inlet 13 and the third injection hole 13a is opened, the refrigerant in the second compression chamber 183 can be injected. through the third injection hole 13a.

As described above, the opening and closing of the third injection hole 13a refers to an opening and gradual closing of the third injection hole 13a as a function of the orbiting movement of the envelope 132 of the orbiting scroll, rather than an idea of all or nothing. Once the refrigerant is injected through the third injection hole 13a, the compression continues as the second compression chamber 183 moves counterclockwise, and then the refrigerant can be discharged through the discharge orifice 121 once it has been completed the compression.

The position of the first injection inlet 11 or of the first injection orifice 11a can be established in the position in which the first injection orifice 11a is opened before the suction of the refrigerant is completed through the suction unit 10a, that is, before the inhalation chamber is complete or closed.

In particular, in a fixed spiral 120 a central part or part C1 of the center of masses and a central part C2 corresponding to a center of the suction unit 10a are formed. The mass center part C1 can be understood as a position representing the center of gravity of the fixed spiral 120 or of the main frame 140. For example, the mass center part C1 may correspond to a central part of the hole 121 of discharge. For the convenience of the description, the part C1 of the center of mass may be called "first central part", and the central part C2 may be referred to as the "second central part".

The fixed scroll 120 includes a plurality of holding units 190 coupled to the main frame 140. The number of holding units 190 may be an even number. For example, as illustrated in Figure 6, the plurality of clamping units 190 are set to four, including a first clamping unit 190a, a second clamping unit 190b, a third clamping unit 190c and a fourth clamping unit 190d. subject, which are separated from each other. However, the number of clamping units 190 is not limited thereto, and clamping units 190 may be set to a number of six, eight or twelve.

The first clamping unit 190a and the second clamping unit 190b may be located on one side with respect to a second extension line 2, and the third clamping unit 190c and the fourth clamping unit 190d may be located on the other side. side with respect to the second extension line 12.

The fixed scroll 120 may be connected to the main frame 140 through the plurality of holding units 190, and may thus be supported on an upper side of the main frame 140 in a balanced state.

Furthermore, the mass center part C1 of the fixed spiral 120 may be established at a point where a first line connecting two facing clamping units and a second line connecting the other two facing clamping units intersect. That is, the mass center part C1 may be established at a point at which the first line connecting the first clamping unit 190a with the third clamping unit 190c and the second line connecting the second unit 190b of the first connecting line 190b intersect. clamping with the fourth clamping unit 190d.

A virtual line extending from the first central part C1 to the second central part C2 is called the first extension line 11, and a virtual line extending from the first central part C1 to a direction perpendicular to the first line of Extension 11 is called second extension line 12.

The first injection inlet 11 or the first injection orifice 11a can be made in a position in which the first extension line 11 is rotated at a first set angle 01 in the clockwise direction with respect to the first central part C1. In this case, the clockwise direction is understood as the direction opposite to the sense of rotation of the compression chamber. That is, the direction of rotation of the compression chamber corresponds to a counterclockwise direction.

For example, the first set angle 01 has a value in the range of 61 ° to 101 °. Furthermore, when the first injection inlet 11 or the first injection orifice 11a are at the first set angle 01, the opening of the first injection orifice 11a can be initiated before the time point at which the suction of the refrigerant has been completed. That is, a temporary point where the inhalation chamber has been completed.

In particular, when at a time point at which the suction of the refrigerant through the suction unit 10a is finished, it is taken as the time point at which the rotation angle of the rotation axis 150 is 0 °, the opening of the first injection orifice 11a can be initiated when the angle of rotation of the rotation axis 150 is in the range of -50 ° to -10 °. That is, a range of the first set angle 01 may correspond to a range of -50 ° to -10 ° based on the rotation angle of the rotation axis 150.

In this case, when the angle of rotation of the rotation axis 150 measures 0 °, the suction of the refrigerant has been completed, the degree of opening of the first injection orifice 11a has been gradually increased and the injection is continued while increasing to 10. ° or 20 ° the angle of rotation of the same and, in addition, the compression of the refrigerant continues. In this case, the compression of the refrigerant is understood as "primary compression".

That is, even though the first injection hole 11a for starting the injection of the refrigerant is opened before the suction of the refrigerant through the suction unit 10a has finished, a temporary point at which the first injection orifice 11a is completely open and the amount of the coolant injection has increased may be a temporary point at which the refrigerant is compressed after the injection of the same through the suction unit 10a has finished.

Accordingly, compression of the refrigerant in the compression chamber is achieved even though the injection orifice has gradually opened after a predetermined time and the injection has finished. Therefore, according to the description, when the injection hole is opened too late, the pressure of the compression chamber has already been increased to a predetermined pressure or more, that is, the internal resistance of the compression chamber has increased , and therefore the problem can be avoided that the amount of flow suitable for the injection can be reduced by the difference in pressures.

On the other hand, the second injection inlet 12 or the second injection orifice 12a can be made in a position rotated at a second set angle 02, counterclockwise from a position of the first injection inlet 11 or the first orifice 11a of injection. For example, the second set angle 02 may have a value in the range of 130 ° to 150 °.

In essence, when the first injection inlet 11 and the second injection inlet 12 have a phase difference of 180 ° or more, a compression chamber in which the refrigerant is injected through the first injection inlet 11 and the another compression chamber in which the refrigerant is injected through the second injection inlet 12 may be separated from each other.

That is, when the phase difference is 180 ° or more, the first injection orifice 11a may be occluded by the envelope 132 of the orbiting scroll at a time point at which the second injection orifice 12a is opened. In this way, it is possible to avoid simultaneous injection into the same coolant compression chamber with intermediate pressures different from one another (for example, by a phenomenon of overlap of injection holes).

However, as envisaged in the embodiment, in a case in which three injections of refrigerant are made before the refrigerant is discharged after the aspiration of the refrigerant, when the first injection inlet 11 and the second injection inlet 12 have a phase difference of 180 ° or more, the position of the third injection inlet 13 is very close to the discharge orifice 121 and, therefore, a problem may arise because the refrigerant in the compression chamber recedes third injection flow path 71 (see Figure 5).

Therefore, in the embodiment, even if the phenomenon of overlap of injection orifices occurs, the degraded capacity of the compressor is minimized by reducing the degree of superposition. For this purpose, at the moment of the superimposition of the injection orifices, the rotation angle of the rotation shaft 150 during the superimposition of the injection orifices is limited to a maximum of 50 ° (see Figure 4).

When the rotation angle of the rotation axis 150 measures 50 °, the second set angle 02 reaches 130 °. On the other hand, when the angle of rotation of the rotational axis 150 measures 30 °, the second set angle 02 reaches 150 °. Accordingly, when the second injection orifice 12a begins to open, the first injection orifice 11a is in an open state, and when the rotation axis 150 rotates by an amount of 30 ° to 50 ° after the second injection orifice injection has been opened, the first injection hole 11a be closed. That is, the phenomenon of superposition of the first injection hole 11a and the second injection hole 12a can occur.

On the other hand, during the injection of the refrigerant through the second injection orifice 12a, the compression of the compression chamber continues. In this case, the compression of the refrigerant is understood as "secondary compression".

The third injection inlet 13 or the third injection hole 13a may be made in a position rotated at a third set angle 03, counterclockwise from a position of the first injection inlet 11 or the first injection orifice 11a. For example, the third set angle 03 has a value in the range of 260 ° to 300 °. The interval of the third established angle 03 can be understood as a determined value taking into account the phenomenon of superposition of injection orifices described above.

That is, when the third injection hole 13a begins to open, the second injection port 12a is in an open state. When the rotation shaft 150 further rotates by an amount of 30 ° to 50 ° after the third injection hole 13a has been opened, the second injection orifice 12a may be closed. That is, the superposition phenomenon of the second injection orifice 12a and the third injection orifice 13a may occur.

On the other hand, during the injection of the refrigerant through the third injection hole 13a, the compression of the compression chamber continues. In this case, the compression of the refrigerant is understood as "tertiary compression".

After the injection of the refrigerant through the third injection hole 13a has been completed, that is, after the third injection hole 13a has been closed, the compression chamber can be further compressed while rotating counterclockwise. In this case, the compression of the refrigerant is understood as "quaternary compression". The refrigerant on which the quaternary compression has been completed can be discharged to the outside of the spiral 120 through the discharge orifice 121.

Figure 4 is a graph illustrating the variation of performance as a function of the angle of a rotation axis that rotates while the second and third injection inlets are simultaneously open, according to a first embodiment.

With reference to Figure 4, as regards the phenomenon of superposition of the injection orifices described above, while the second and third holes 12a and 13a, of injection, are simultaneously open, on the horizontal axis the angle is represented of rotation of rotation axis 150. In Figure 4, although it is described based on the phenomenon of superposition of the second and third holes 12a and 13a, injection, can be applied to the phenomenon of superposition of the first and second holes, 11a and 12a, injection.

Also, depending on the variation of the angle on the horizontal axis, factors related to the performance of the compressor 10 or of the air conditioner 1 are represented on a vertical axis. In particular, the factors represented on the vertical axis can include the average power (in kW) of the air conditioner 1, the average performance coefficient (COP) and the pressure of the refrigerant discharged from the compressor 10, that is, the high pressure fluctuation (in kPa).

In the injection of refrigerant with different pressures intermediate to each other, a change in pressure occurs depending on the mixture of the refrigerant existing in the compression chamber and the injected refrigerant. The high pressure fluctuation (in kPa) refers to the fluctuation of the high pressure discharged caused by the variation of the pressure. The fluctuation can be understood as a difference between a maximum value and a minimum value of the high pressure discharged.

Until the angle of rotation of the rotation axis 150 does not reach 50 °, that is, at those angles in which the second and third holes 12a and 13a, of injection, are simultaneously open, the average power of the air conditioner 1 and the high pressure fluctuation may not vary significantly, and the average coefficient of performance (COP) may increase slightly.

However, when the angle of rotation of the rotation shaft 150 is greater than 50 °, for example when the angle of rotation is 60 °, the average efficiency coefficient of the air conditioner 1 decreases significantly, and the average power also decreases. In addition, the fluctuation of high pressure increases significantly. When the high pressure fluctuation increases, the operating stability and reliability of the compressor can decrease, and the performance of the air conditioner can decrease. Therefore, it is preferred to maintain the angle of rotation of the rotation shaft 150 by 50 ° or less.

On the other hand, the rotation angle of the rotation shaft 150 can be maintained at 30 ° or more. In particular, when the angle of rotation of the rotation axis 150 is maintained at 30 ° or less, as described above, the phase difference between two injection inputs is close to 180 °, the position of the third inlet 13 of injection is very close to a discharge pressure of the refrigerant and, therefore, a problem may arise in the sense that the injection of the refrigerant through the third injection inlet 13 is limited.

Therefore, the position of the third injection inlet 13 is preferably maintained at 250 ° or less, based on the temporary point of completion of the suction (see Figure 5). In view of this, the angle of rotation of the rotation axis 150 can be set in the range of 30 ° to 50 ° and, consequently, the second set angle 02 can be set in the range of 130 ° to 150 ° and the The third set angle 03 may be set in the range of 260 ° to 300 °.

Figure 5 is a graph illustrating the manner in which the internal pressures of the first and second compression chambers vary according to a first embodiment, as a function of the angle of the axis of rotation.

With reference to Figure 5, the graph in which the variation of the pressure in the first and second chambers, 181 and 183, of compression as a function of the rotation angle of the rotation axis 150, according to a first embodiment is illustrated. . When the rotation angle of the rotation axis 150 is 0 °, the suction of the refrigerant has ended and, therefore, indicates the time point at which an inhalation chamber is complete. The internal pressures of the first and second compression chambers 181 and 183 can be increased gradually while the first and second compression chambers 181 and 183 move as the angle of rotation increases. The first compression chamber 181 and the second compression chamber 183 are compressed while moving, and have a phase difference 0d. For example, the phase difference 0d is approximately 180 °.

Further, when the angle of rotation is increased by an established angle, for example, when the angle of rotation is represented by 0e (approximately 630 °), the internal pressure of the compression chamber increases sharply. In this case, the rotation shaft 150 may have rotated approximately three rotations (1080 °) until the refrigerant is discharged through the discharge orifice 121 after the refrigerant has been drawn through the suction unit 10a.

When the third injection inlet 13 is located in a position in which the internal pressure of the compression chamber is significantly increased, the internal pressure (internal resistance) of the compression chamber is greater than the pressure of the injected refrigerant or the The difference between the two is not great, problems can arise due to the injection of refrigerant through the third injection hole 13a being limited since a return of the refrigerant from the compression chamber to the third injection inlet 13 can occur.

Therefore, the third injection inlet 13 may be practiced in a position of 250 ° or less in a direction of compression of the coolant as a starting point, a position before the internal pressure of the compression chamber is significantly increased, for example a position in which the suction of the coolant is completed.

In particular, referring to Figure 5, the zones represented by thick lines in the graph of the pressure variations of the first and second compression chambers indicate periods in which the third injection hole 13a is open to the first chamber 181 of compression or to the second compression chamber 183 when the third injection inlet 13 is at an angle of 250 °.

In this case, the final part of the period in which the third injection hole 13a is open to the first compression chamber 181 corresponds to the angle 0e of rotation of the axis of rotation in which the pressure of the first compression chamber 181 increases sharply. Therefore, when the third injection inlet 13 is positioned at an angle of 250 ° or more, the problem may arise that the refrigerant is injected even after a time point at which the internal pressure of the first compression chamber 181 It has increased significantly. Therefore, according to the embodiment, the third injection inlet 13 is made and positioned at an angle of 250 ° or less.

When the third injection inlet 13 is located at an angle of 250 °, the third set angle 03 may correspond to 300 °. In addition, a position of the third injection inlet 13 when the third set angle 03 is 260 ° may correspond to a position corresponding to a state in which the angle of rotation of the rotation axis 150 is maintained at 50 ° or less, having Consider the phenomenon of superposition of the injection holes.

Therefore, since the injection of the refrigerant is done through three injection inlets, the injection flow quantity can be increased and the positions of the three injection inlets optimized, and the performance of the compressor and the conditioner can be improved of air.

Figure 6 is a system diagram illustrating a flow state of a refrigerant during heating operation of an air conditioner according to a first embodiment.

With reference to Figure 6, when the air conditioner 1 performs the heating operation, the refrigerant sucked into the compressor 10 through the suction unit 10a is compressed to mix it with the refrigerant injected into the compressor 10 through the first path 51. of injection flow. The process until the refrigerant is mixed with the injected refrigerant after the refrigerant has been sucked into the compressor 10 is called "primary compression". The compressed refrigerant is compressed again by the primary compression, and the compressed refrigerant is mixed with the refrigerant injected into the compressor 10 through the second injection flow path 61. This process is called "secondary compression".

The compressed refrigerant is compressed again by secondary compression, and the compressed refrigerant is mixed with the refrigerant injected into the compressor 10 through the third injection flow path 71. This process is called "tertiary compression".

The compressed refrigerant is compressed again by the tertiary compression and, in this case, the compression process is called "quaternary compression". Thus, in the case of heating operation, three injection processes and four compression processes are carried out. In the compressor 10, the refrigerant compressed by the tertiary compression can flow to the indoor heat exchanger 40 through the switching unit 15 of the flow path, and the condensed refrigerant in the indoor heat exchanger 40 passes through the third exchanger 70 interior of heat.

In this case some coolant (the third diverted coolant) is diverted to expand in the third injection expansion unit 75. The expanded refrigerant in the third injection expansion unit 75 exchanges heat with the main refrigerant. In this process, the main refrigerant is supercooled, and the third diverted refrigerant can be injected to the compressor 10 through the third injection inlet 13.

In this case, the injection valve 78 is open and the bypass valve 85 is closed, and the refrigerant which is introduced into the third injection flow path 71 passes through the injection valve 78 and, thus, may be injected to the compressor 10.

On the other hand, the main refrigerant that has passed through the third indoor heat exchanger 70 passes through the second indoor heat exchanger 60, and some refrigerant (the second diverted refrigerant) is diverted to expand in the second unit 65 injection expansion. The expanded refrigerant in the second injection expansion unit 65 exchanges heat with the main refrigerant. In this process, the main refrigerant is supercooled and the second diverted refrigerant can be injected into the compressor 10 through the second injection inlet 12.

The main refrigerant that has passed through the second interior heat exchanger 60 passes through the first indoor heat exchanger 50, and some refrigerant (the first diverted refrigerant) is diverted to expand in the first expansion unit 55. injection. The expanded refrigerant in the first injection expansion unit 55 exchanges heat with the main refrigerant. In this process, the main refrigerant is supercooled, and the first diverted refrigerant can be injected to the compressor 10 through the first injection inlet 11.

The main refrigerant which has passed through the first indoor heat exchanger 50 expands in the first expansion device 30 and then evaporates in the heat exchanger 20, and can be sucked into the suction unit 10a of the compressor 10 to through the flow switching unit 15.

Thus, when the air conditioner 1 performs the heating operation, three injections of refrigerant are passed through the plurality of internal heat exchangers 50, 60 and 70, and it is possible to increase the amount of refrigerant in circulation of the refrigerant system. Consequently, it can improve the heating capacity of the system.

On the other hand, as described above, to perform the injection of the refrigerant during the heating operation of the air conditioner, it can be controlled so that the first, second and third, 55, 65 and 75 expansion units of injection are open and the injection valve 78 is open. However, when it is not required for the injection of the refrigerant, for example, when the outside air temperature is higher than a set temperature or the load of the indoor unit is not large, the heating operation of the air conditioner can be controlled. air so that the first, second and third, 55, 65 and 75, injection expansion units are closed and the injection valve 78 is closed and, therefore, injection can not be performed.

Figure 7 is a diagram illustrating a flow state of a refrigerant during refrigeration operation of an air conditioner according to a first embodiment.

Referring to Figure 7, the air conditioner 1 performs a cooling operation, and the refrigerant sucked into the compressor 10 through the suction unit 10a is compressed to mix it with the refrigerant injected into the compressor 10 through the first path 51. of injection flow. This process is called "primary compression".

The compressed refrigerant is compressed again by the primary compression, and the compressed refrigerant is mixed with the refrigerant injected into the compressor 10 through the second injection flow path 61. This process is called "secondary compression".

The compressed refrigerant is compressed again by secondary compression, and the compression process is referred to as "tertiary compression" in this case. The refrigerant compressed by the secondary compression is discharged from the compressor 10 and is introduced into the heat exchanger 20 through the flow switching unit 15.

On the other hand, the injection of the refrigerant through the third injection inlet 13 may not be performed.

The condensed refrigerant in the heat exchanger 20 passes through the first indoor heat exchanger 50, and some of the refrigerant (the first diverted refrigerant) is diverted to expand in the first injection expansion unit 55. The expanded refrigerant in the first injection expansion unit 55 exchanges heat with the main refrigerant, and in this process the main refrigerant is supercooled and the first diverted refrigerant can be injected into the first injection inlet of the compressor 10.

The main refrigerant that has passed through the first indoor heat exchanger 50 passes through the second indoor heat exchanger 60, and some refrigerant (the second diverted refrigerant) is diverted to expand in the second heat expansion unit 65. injection. The expanded refrigerant in the second injection expansion unit 65 exchanges heat with the main refrigerant. In this process, the main refrigerant is supercooled and the second diverted refrigerant can be injected into the compressor 10 through the second injection inlet 12.

The main refrigerant which has passed through the second interior heat exchanger 60 passes through the third interior heat exchanger 70, and the third diverted refrigerant is diverted to expand in the third injection expansion unit 75. The expanded refrigerant in the third injection expansion unit 75 exchanges heat with the main refrigerant. In this process, the main refrigerant is supercooled and the third diverted refrigerant is sucked into the suction unit 10a of the compressor 10 through the bypass path 80.

According to this embodiment, the injection valve 78 is closed and the bypass valve 85 is open, and the refrigerant which is introduced into the third injection flow path 71 passes through the bypass valve 85 and can be sucked into the compressor 10

In other words, during the cooling operation, the injection process on the high pressure side is limited and the refrigerant is sucked into the compressor 10, and thus the degree of supercooling can be further ensured. In this way, since the refrigerant pressure is reduced to the suction pressure (e.g., low pressure) of the compressor 10 in the third injection expansion unit 75, and the decompressed refrigerant is caused to exchange heat with the main refrigerant in the third interior heat exchanger 70, the overcooling effect can be further improved.

On the other hand, the main refrigerant which has passed through the third indoor heat exchanger 70 expands in the second expansion device 35 and then evaporates in the indoor heat exchanger 40, and can be sucked into the compressor 10 through the heat exchanger. the flow switching unit 15. Accordingly, in the combination unit 83 it can be combining the refrigerant that has passed through the indoor heat exchanger 40 with the refrigerant that has passed through the bypass flow path 80, and can then be sucked into the compressor 10.

When the air conditioner 1 performs cooling operation, the evaporation pressure increases due to the relatively high temperature of the outside air. The difference between low pressure and high pressure during cooling operation is less than during heating operation and, therefore, an effect in which a plurality of injections are performed (eg, three times) on the compressor 10 may be limited by considering a point at which the injection flow quantity corresponding to the difference between low pressure and high pressure is determined.

Therefore, the injection of the refrigerant on the high pressure side is omitted and direct suction is made in the compressor 10, and thus the advantage is obtained that the degree of supercooling can be further guaranteed.

A bypass flow path extending from the first injection flow path 51 or the second injection flow path 61 to the suction unit 10 of the compressor 10 may be additionally provided. In this configuration, although it may be desired that in FIG. the compressor 10 performs only a single injection and two flow paths are directly drawn into the suction unit 10a of the compressor 10, such a pipe configuration is difficult, and an additional valve is required, which raises the costs.

The noise generated by the indoor unit can be reduced if the degree of supercooling is increased during cooling operation, the heat exchange efficiency of the system is increased and the refrigerant introduced into the indoor heat exchanger is in the liquid state or a state in which the degree of dryness is low.

In the following a second embodiment of the present description will be described. Some of the features of the second embodiment are different from those of the first embodiment. The characteristics that are different are described here. As for the characteristics of the second embodiment which are the same as those of the first embodiment, reference will be made to the descriptions and reference numbers of the first embodiment.

Figure 8 is a system diagram illustrating a configuration of an air conditioner according to a second embodiment.

With reference to Figure 8, an air conditioner 1 according to the second embodiment includes a first phase separator 150 connected to the first injection flow path 51, a second phase separator 160 connected to the second injection flow path 61, and an internal heat exchanger 170 connected to the third injection flow path 71.

For the description of the interior heat exchanger 170, reference will be made to the description of the third interior heat exchanger 70 of the first embodiment.

The first phase separator 150 and the second phase separator 160 are understood as devices separating the circulating refrigerant, liquid refrigerant and gaseous refrigerant. The gaseous refrigerant separated in the first phase separator 150 can flow to the first injection flow path 51, and the separated gas refrigerant in the second phase separator 160 can flow into the second injection flow path 61.

The phase separator 150 and the indoor heat exchanger, which are devices that separate the refrigerant circulating in the air conditioner, are referred to as "refrigerant separation devices".

According to embodiments of the present disclosure, the amount of refrigerant injected into a compressor is adjusted according to the mode of operation of the air conditioner, which results in an effective injection and a sufficient degree of supercooling.

In particular, during heating operation, the amount of refrigerant circulation can be increased by injecting refrigerant into the compressor three times.

During cooling operation, the advantage is obtained that the injection of refrigerant to the compressor can be done twice, which provides supercooling. In particular, a bypass flow path that can bypass an injection flow path is provided, and the refrigerant that has passed through the indoor heat exchanger is diverted through a compressor suction unit during cooling operation. , which provides overcooling.

In addition, since the refrigerant compressor configured to have an intermediate pressure is injected, the electrical energy required when compressing the refrigerant in the compressor can be reduced and, therefore, an advantage is obtained because the efficiency of the compressor can be increased. cooling and heating.

Claims (11)

1. An air conditioner (1) comprising: a compressor (10) for compressing a refrigerant, the compressor having a suction unit (10a) and a plurality of injection inlets (11, 12, 13); an internal heat exchanger (40) in which the compressed refrigerant is introduced during a heating operation; an external heat exchanger (20) in which the compressed refrigerant is introduced during a cooling operation; a plurality of refrigerant separation devices (50, 60, 70) through which a condensed refrigerant passes in the indoor heat exchanger or in the outdoor heat exchanger; a plurality of injection flow paths (51, 61, 71) extending from the plurality of refrigerant separation devices (50, 60, 70) to the plurality of injection inlets (11, 12, 13); Y a bypass flow path (80) extending from one of the plurality of injection flow paths (51, 61, 71) to the aspiration unit (10a), wherein the plurality of injection inlets (11, 12) comprises a first injection inlet (11) and a second injection inlet (12), the plurality of refrigerant separation devices (50, 60) includes a first interior heat exchanger (50) of heat and a second internal heat exchanger (60), and the plurality of injection flow paths (51, 61) includes a first injection flow path (51) and a second flow path (61) of injection, characterized in that : the plurality of injection inlets (11, 12, 13) further comprises a third injection inlet (13), the plurality of refrigerant separation devices (50, 60, 70) further includes a third internal heat exchanger (70) , and the plurality of injection flow paths (51, 61, 71) further includes a third injection flow path (61), wherein said first injection flow path (51) is connected to the first inner exchanger (50). ) of heat to inject into the compressor (10) a coolant having a first ^{intermediate pressure; said second injection flow path (} 61 ^{) is connected to the second} internal heat ^exchanger (60) for injecting into the compressor (10) a refrigerant having a second intermediate pressure; and said third injection flow path (71) is connected to the third internal heat exchanger (70) to inject into the compressor (10) a refrigerant having a third intermediate pressure, and the second intermediate pressure is higher than the first intermediate pressure and the third intermediate pressure is higher than the second intermediate pressure. The air conditioner (1) according to claim 1, wherein the bypass flow path (80) extends from a branch unit of the third injection flow path (71) to the suction unit (10a) . 3. The air conditioner (1) according to claim 2, further comprising: a bypass valve (85) disposed in the bypass flow path (80); Y an injection valve (78) disposed in the third injection flow path (71). The air conditioner according to claim 3, wherein the bypass valve (85) is closed and the injection valve (78) is open during a heating operation, and wherein the bypass valve (85) is open and the injection valve (78) is closed during a cooling operation. 5. The air conditioner (1) according to any one of claims 1 to 4, wherein: the compressor (10) includes a scroll compressor having a fixed scroll (120) and an orbiting scroll (130); and said first injection inlet (11) is disposed on a first side of the fixed spiral (120) for injecting a refrigerant into a compression chamber; said second injection inlet (12) is arranged on a second side of the fixed spiral (120) to inject into the compression chamber a refrigerant having a pressure different from that of the refrigerant injected into the first injection inlet (11) in ; Y said third injection inlet (13) is arranged on a third side of the fixed spiral (120) to inject into the compression chamber a refrigerant having a pressure different from that of the refrigerant injected in the first and second inlets (11, 12). ) of injection. The air conditioner (1) according to claim 5, wherein the first injection inlet (11) is disposed in a position in which an extension line connecting a central part of the fixed spiral (120) to a The central part of the suction unit (10a) is rotated at a first set angle (01) in a direction opposite to the direction of rotation of the compression chamber. The air conditioner (1) according to claim 6, wherein the first established angle (01) measures from 61 ° to 101 °. The air conditioner (1) according to claim 5, wherein the second injection inlet (12) is disposed in a position that is rotated in a direction of rotation of the compression chamber at a second set angle (02) from a position of the first injection inlet (11). The air conditioner (1) according to claim 8, wherein the second established angle (02) measures from 130 ° to 150 °. The air conditioner (1) according to claim 5, wherein the third injection inlet (13) is disposed in a position that is rotated in a direction of rotation of the compression chamber at a third set angle (03) from a position of the first injection inlet (11). The air conditioner (1) according to claim 10, wherein the third set angle (03) measures from 260 ° to 300 °.